EP0100951A1 - Piquet basculant - Google Patents

Piquet basculant Download PDF

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Publication number
EP0100951A1
EP0100951A1 EP83107254A EP83107254A EP0100951A1 EP 0100951 A1 EP0100951 A1 EP 0100951A1 EP 83107254 A EP83107254 A EP 83107254A EP 83107254 A EP83107254 A EP 83107254A EP 0100951 A1 EP0100951 A1 EP 0100951A1
Authority
EP
European Patent Office
Prior art keywords
spring
tilting rod
joint
rod according
tilting
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP83107254A
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German (de)
English (en)
Other versions
EP0100951B1 (fr
Inventor
Immanuel Straub
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Straub Federnfabrik AG
Original Assignee
Straub Federnfabrik AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Straub Federnfabrik AG filed Critical Straub Federnfabrik AG
Priority to AT83107254T priority Critical patent/ATE30121T1/de
Publication of EP0100951A1 publication Critical patent/EP0100951A1/fr
Application granted granted Critical
Publication of EP0100951B1 publication Critical patent/EP0100951B1/fr
Expired legal-status Critical Current

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Classifications

    • A—HUMAN NECESSITIES
    • A63—SPORTS; GAMES; AMUSEMENTS
    • A63C—SKATES; SKIS; ROLLER SKATES; DESIGN OR LAYOUT OF COURTS, RINKS OR THE LIKE
    • A63C19/00—Design or layout of playing courts, rinks, bowling greens or areas for water-skiing; Covers therefor
    • A63C19/06—Apparatus for setting-out or dividing courts
    • A63C19/062—Slalom gate poles, posts or marking sticks for sport fields
    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01F—ADDITIONAL WORK, SUCH AS EQUIPPING ROADS OR THE CONSTRUCTION OF PLATFORMS, HELICOPTER LANDING STAGES, SIGNS, SNOW FENCES, OR THE LIKE
    • E01F9/00—Arrangement of road signs or traffic signals; Arrangements for enforcing caution
    • E01F9/60—Upright bodies, e.g. marker posts or bollards; Supports for road signs
    • E01F9/623—Upright bodies, e.g. marker posts or bollards; Supports for road signs characterised by form or by structural features, e.g. for enabling displacement or deflection
    • E01F9/627—Upright bodies, e.g. marker posts or bollards; Supports for road signs characterised by form or by structural features, e.g. for enabling displacement or deflection self-righting after deflection or displacement
    • E01F9/629—Traffic guidance, warning or control posts, bollards, pillars or like upstanding bodies or structures

Definitions

  • the invention relates to a tilting rod, in particular a slalom tilting rod, with a first rod part, a second rod part and a helical spring fastened to the first rod part and to the second rod part, the part of which does not serve to secure the attachment forms a spring joint.
  • a tilting rod in particular a slalom tilting rod
  • the first rod part serves as a floor anchoring part
  • the second rod part forms the pivot rod.
  • a slalom tilting rod of this type is already known.
  • the result of this spring joint is that the rod is not knocked over or tilted when it is touched, but merely yields resiliently and then returns to the original position.
  • it is disadvantageous that the slalom tilting rod continues to vibrate for a long time after the turn. These shrinkages can lead to the fact that the ground anchoring part inserted in the snow loosens. There is then a risk that the slalom tilting rod will be torn out of the snow on another turn.
  • a disadvantage is also that after a strong sticking, for example by freezing, the B odenverarik fürimisteilsdie spring of the spring joint can be pulled apart when attempting to withdraw the rod out of the snow.
  • this is achieved in the case of a tilting rod of the type mentioned at the outset in that at least one active member is provided which stresses the coil spring turns of the spring joint.
  • This configuration avoids the disadvantages of using a helical spring as a spring joint. If the tilt rod is tilted, it returns to its original position after a few short vibrations. There is no risk of locking if the tilt position is more than 90 °. A much larger turn is even possible. With each turn, the turns open evenly because, in contrast to the individual disks of the known slalom tilting rod described above, they are connected to one another.
  • the active member is expediently arranged at the end or in the vicinity of one end of the spring joint and acts on the other end of the helical spring forming the spring joint via a tension member. This results in a particularly simple construction. The same also applies to an embodiment in which, for reasons of symmetry, one active member is arranged at the ends of the helical spring and these members are connected to one another via a tension member.
  • the active member is expediently formed by a compression spring.
  • Compression springs are relatively inexpensive to manufacture.
  • the compression spring advantageously has a larger wire cross section than the helical spring forming the spring joint. This makes it possible to keep the diameter of the spring joint small and to exert such a force on this spring joint that the swivel rod quickly and after a deflection is returned to the original position without long vibrations.
  • the compression springs expediently have a smaller diameter than the spring joint or the attachment lugs, so that they can move unimpeded by the tilt rod. So that the compression spring and the coil spring forming the spring joint form a unit that is conveniently suitable for connecting the rod parts, it is advantageous that at least one turn of the compression spring is clamped between turns of the coil spring.
  • the respective compression spring can also consist of one piece with the coil spring forming the spring joint. In this case, it is sufficient to wind a single spring, which is then able to perform several functions.
  • the helical spring can have a fastening projection on both sides of the part serving as a spring joint.
  • this fastening attachment can be pressed or screwed into the first rod part or into the second rod part, which normally each consist of a piece of plastic tube. This enables the tilt rod to be manufactured cheaply.
  • the fastening attachment is expediently part of the coil spring. This makes the production of the slalom tilting rod cheaper. It is advantageous if the respective attachment projection has a smaller diameter than the part of the coil spring that forms the spring joint. The larger diameter of the part serving as a spring joint contributes to the stability of the tilting rod.
  • a relatively small force of the compression spring is then sufficient, which can then also be formed as part of the helical spring forming a spring joint. If, however, it is required that the tilting rod has the same diameter over its entire length, it is expedient if the respective fastening attachment has the same diameter as the part forming the spring joint. In this case it is also possible to cover the spring joint without the diameter in this area becoming larger than that of the rest of the rod.
  • the fastening attachment is fastened by pressing it into a rod part, it expediently has at least one turn which has a somewhat larger diameter than the rest of the attachment. This enables better anchoring in the plastic pipe. Good anchoring is necessary so that e.g. when pulling the tilt rod out of the snow or out of the ground the coil spring is not torn from one of the rod parts.
  • the spring joint part expediently has a practically conical end section at both ends. This results in a gradual transition from the spring joint part to the fastening part, which improves the functionality of the spring joint part.
  • the spring joint part expediently has a cylindrical section between the conical end sections. It is primarily the cylindrical section that deforms when the rod tilts and ensures that the rod returns to the practically exactly same position afterwards.
  • the coil spring or the compression spring can consist of round wire. This results in the lowest manufacturing costs and enables the helical spring to be screwed into a thread of the respective rod part. However, it is also possible to manufacture the coil spring and / or the compression spring from square wire. This enables an even better use of the available limited space and brings about greater positional stability. With regard to the positional stability - it should be noted that after a tilting the rod never returns to the exact same position as before, because the individual turns of the spring joint rub against each other and thus assume slightly different positions each time.
  • a helical spring coaxially to the helical spring, a helical spring, the windings of which have a winding direction which is opposite to that of the windings of the former helical spring and fit snugly against the windings of the former helical spring, at least in the area of the spring joint.
  • the second coil spring is arranged within the first-mentioned coil spring and does not have coils which abut one another. Due to the design described, the tilting rod has a high positional stability. Because the second coil spring lies with its windings on the windings of the spring joint, it causes the windings of the spring joint to be guided so that, after the spring joint has bent, they are practically returned to the same position that they previously held.
  • the dimensional stability of a tilting rod can possibly be impaired by the compression spring, because it has a tendency to curve because of the force exerted by the tension member. This curvature can then be transferred to the relatively soft plastic tube and thus also cause the tilting rod to curve.
  • a straight holder can be provided for the compression spring. This advantageously consists of a twisted sheet metal strip of practically the same width as the inside diameter of the compression spring. It thus prevents the same from bending out to either side and, because it is movable in the tension spring, can at the same time form part of the tension member which is held under tension by the compression spring.
  • the tension member can be or have a chain.
  • a chain has the advantage that it is sufficient to cut a piece from the chain material, the end links of the chain then serving as a fastening element.
  • a cable as a tension member, e.g. a steel cable, or a corresponding element made of plastic.
  • the attachment lugs can be screwed into a thread of the respective rod part. This simplifies the assembly of the tilt rod. If necessary, the joint unit can also be easily replaced.
  • a vibration damping device which e.g. acts on the spring joint. This makes it possible to effectively dampen the vibrations of the tilting rod and gives the designer greater freedom in the design of the spring joint. For example, when using a vibration damper, the diameter of the spring joint can be kept relatively small without this being bought at the expense of a disproportionately long decay time.
  • a vibration damper device which is formed by a friction member that can be moved back and forth inside the slalom tilting rod, is particularly recommended for cost reasons.
  • a friction member can be manufactured cheaply and uses e.g. the plastic tube inner wall as a friction surface.
  • the friction member advantageously consists of a cylindrical jacket-shaped resilient sheet metal piece which is coupled to the free end of the compression spring and rubs against the inner wall of the slalom tilting rod during its movement.
  • Such a friction member is very cheap to manufacture and can be easily assembled using the same means as the tension member.
  • a friction member which consists of a tubular, resilient piece of sheet metal which is coupled to the free end of the compression spring and bears against the windings of this compression spring with prestress and rubs against it during its movement.
  • a friction member which consists of a tubular, resilient piece of sheet metal which is coupled to the free end of the compression spring and bears against the windings of this compression spring with prestress and rubs against it during its movement.
  • the sleeve which is formed by the resilient piece of sheet metal, has a stabilizing effect on the compression spring, which under the tension caused by the tension member has the tendency to deflect laterally and to transmit this deflection to the plastic tube of the rod. Further measures to stabilize the compression spring can therefore be omitted.
  • the vibration damping device according to the invention can also be used for tilt rods which have a different joint design than a spring joint.
  • FIGS. 1 and 2 of a tilting rod 10 intended for use as a slalom tilting rod has a first rod part 11 designed as a floor anchoring part, which is connected via a spring joint 13 to a second rod part 15 designed as a pivoting rod.
  • This connection enables the pivoting rod 15 to be pivoted in any direction.
  • Both the floor anchoring part 11 and the swivel rod 15 consist of a light plastic tube, the free ends of which are each closed by a pin 17.
  • plastic pipe other pipe or rod materials, e.g. Wood or aluminum. However, the use of plastic is preferred.
  • the spring joint 13 is formed by a helical spring 19, which in addition to the spring hinge portion 13 further sections 21, 23 (Fi g .2) with special functions have.
  • the sections 21 serve as fastening lugs with which the coil spring 19 is anchored in the floor anchoring part 11 and in the pivot rod 15.
  • the fastening projection 21 is provided with a turn 22 which has a slightly larger diameter than the diameter of the rest of the fastening projection. This is particularly advantageous for anchoring in a plastic pipe. If one is used to produce the slalom tilting rod, the tube end can be softened somewhat, for example by immersing it in hot water, before the attachment 21 is inserted into the tube end. The wide pipe end then adapts to the contours of the attachment projection 21, the plastic tube firmly enclosing the attachment projection 2l after cooling.
  • the sections 23 of the coil spring 19 have a slightly smaller diameter than the fastening sections 21 and serve as active members which stress the spring joint part 13 of the coil spring 19. Sections 23 thus represent compression springs which are connected to one another under tension under tension to fulfill their purpose. As a result, the turns of the spring joint 13 are pressed firmly against one another.
  • the diameter of the sections 23 serving as compression springs is smaller than that of the fastening lugs 21.
  • the turns in the plastic tube 11, 15 can move freely without friction losses due to friction of the turns on the inner wall of the plastic tube.
  • the section 13, which forms the spring joint part can be wound in such a way that the windings lie against one another with a prestress.
  • the size of this preload is limited for design and manufacturing reasons.
  • the preload cannot exceed a certain size for a given spring dimension.
  • the spring joint would be so soft that after a contact with the slalom tilting rod, the vibrations of long duration already mentioned at the beginning would occur. This disadvantage has prompted experts to refrain from the usual spring joints in slalom tilting rods.
  • the spring joint 13 formed from a helical spring 19 is subjected to pressure from an active member 23 in addition to any prestress that may be present, this spring joint is nevertheless stiff enough for the given small dimensions due to the diameter of the slalom rod a contact and deflection of the S lalomkippstange to bring them rapidly and without great and long-lasting vibrations back to the original location.
  • the spring joint part 13 has a conical end section 14 at both ends. Between these end sections 14 there is a cylindrical section 16, the diameter of which approximately corresponds to the outside diameter of the slalom tilting rod or is somewhat larger. With such a configuration, the turns in the cylindrical section with the large diameter primarily open when turning. If the rod then returns to its original position after the bend and the turns come to lie slightly differently on one another, the relatively large diameter of the spring joint has the advantage that the slalom tilting rod again returns to a position that is only imperceptibly different from the original position. Greater positional stability is achieved when using square wire to produce the coil spring 19. As a rule, the positional stability of a spring made of round wire is also sufficient, which is cheaper than a spring with a different wire profile.
  • the described configuration of the coil spring forming the spring joint l3 is extremely simple and cheap. However, it would also be possible to design the compression springs 23 separately. In principle, a single compression spring 23 would also suffice. However, the use of two compression springs has the advantage that the individual compression springs 23 can be made relatively short, so that they do not buckle when pressed together and practically hardly ever come into contact with the tube wall.
  • the active element could also be e.g. a gas spring or other elastically deformable member can be used, which is suitable for compressing the spring joint 13.
  • the tension member 25 consists of a chain which is attached to each end of the spring with a ring 29.
  • the compression springs 23 are tensioned so that the windings in the region 13 are pressed together.
  • the rings 29 used for fastening advantageously consist of about 1 V2 turns of a coil spring. With a suitable dimensioning, the ends of these rings prevent the ring from rotating because they would abut the spring 23 if they were to rotate.
  • FIGS. 3 and 4 The exemplary embodiment of a slalom tilting rod 10 shown in FIGS. 3 and 4 is basically constructed similarly to the slalom tilting rod according to FIGS. 1 and 2. The same reference numbers can therefore be used. However, as a comparison of FIG. 3 with FIG. 2 shows, the joint unit 30 has a somewhat different structure.
  • the spring joint 13 is in turn formed by a helical spring 19 which, apart from not having each a fixing portion 21 to the spring hinge section 13, with which the coil spring 19 in the bottom anchoring part 11 and the S chwenkstab is anchored 15th
  • a threaded section 8, 12 is provided in the respective plastic tube 11, 15, into which section 21 of the coil spring 19 is screwed.
  • the attachment could also be done in the same manner as described in the first embodiment.
  • the coil spring 19 advantageously has the same diameter over the entire length, which simplifies the manufacture of the spring. This also makes it possible for the slalom tilting rod 10 to have the same diameter over its entire length, it also being possible to cover the spring joint.
  • a number of rings 31 are provided for this purpose, which surround the spring joint 13. These rings are advantageously made of plastic. If they are touched by a ski edge, they can turn. This prevents damage to both the spring joint 13 and the skis. There can be no metallic contact between the skis and the slalom tilt rod.
  • the active element is formed by a compression spring 23.
  • the spring rings 29 advantageously consist of approximately 1 V2 turns of a helical spring, the ends of these rings preventing rotation of the ring with a suitable dimensioning, as was already described above with reference to the first exemplary embodiment of the invention.
  • a plastic cable eg made of nylon, or a chain, as shown in FIG. 2, could also be used.
  • a vibration damping device 33 is also provided on the spring joint unit 30. This has the task of damping the movements of the pivot rod 15 after a deflection, so that it will soon return to the original position and in this remains.
  • the vibration damping device is formed by a friction member that can be moved back and forth inside the slalom tilting rod, for example in the floor anchoring part.
  • the friction member consists of a resilient sheet metal piece in the form of a cylinder jacket (FIG. 4), which is coupled to the free end of the compression spring 23 with the ring 29 and rubs against the inner wall of the slalom tilting rod as it moves.
  • the slalom tilting rod is made of plastic.
  • the compression spring 23 and the friction member 33 are arranged in the floor anchoring part 11.
  • the arrangement shown has the advantage that the center of gravity of the slalom tilting rod is very low and the masses moved when the pivoting rod is deflected are kept as small as possible.
  • FIG. 5 A preferred embodiment of the tilt rod 10 is shown in Figures 5 and 6.
  • the structure of the joint unit 30 is the same as that of FIG. 3.
  • the spring joint 13 is in turn formed by a helical spring 19 which, in addition to the spring joint section 13, also has a fastening section 21 with which the helical spring 19 is anchored in the first rod part 11 and in the second rod part 15 is.
  • the respective rod part 11, 15 is advantageously formed by a plastic tube in which a threaded section 8, 12 is provided.
  • This section 23 is designed as a compression spring. In Figure 5, only a section 23 is provided. However, it would be possible, as in FIG. 1, to provide two such sections 23.
  • the spring joint 13 is covered by a number of rings 31 which surround the spring joint 13.
  • the tension member 25, which connects the opposite ends of the helical spring to one another, consists of a chain 25 'and a strip-shaped part 25 "which is twisted as shown in FIG. 5.
  • the strip 25" therefore has a twist as it did arises when one end is clamped and the other end is twisted around the longitudinal axis of the strip.
  • Eyelets 26, 26 ' are provided at the ends of the strip 25 ", one eyelet 26' being used for connection to the chain 25 ', while the other eyelet 26 receives a spring ring 29.
  • the spring rings 29 therefore have the same function as in the other embodiments, namely to fasten the tension member 25 within the spring 19, the compression spring 23 still compressing the windings in the region of the spring joint 13 with additional force.
  • the twisted strip the width of which basically corresponds to the inside diameter of the spring in the region of the compression spring section 23, has a special function. Because section 23 is relatively long, it has the tendency in the construction of FIG. 3 to bend laterally. This can lead to a deformation of the relatively soft pipe section in which it is housed, but this is prevented by the strip 25 ".
  • This Strip 25 '' advantageously exists on sheet metal so that it has sufficient dimensional stability. However, it would also be possible to use another element for the stiffening, for example a tube or a star-shaped profile.
  • the stiffening 25 " is particularly important for designs of the tilting rod where a vibration damping device 33 can be dispensed with or where a vibration damping device of the type according to Figures 3 and 4 is used.
  • the vibration damping device 33 is arranged above the compression spring section 23.
  • the vibration damping device consists of a sleeve 33 which has a slot 34 which extends practically in the longitudinal direction. This bush rests with a certain preload on the section 23 and is connected to the free end of the compression spring section 23 by an embossing 35 engaging in a thread. If section 23 is thus pressed together, sleeve 33 rubs against the windings of compression spring section 23.
  • This configuration has the advantage that friction conditions that remain practically constant are achieved over the entire service life of the tilting rod.
  • both the stiffening member 25 ′′ and the vibration damping device 33 could be used in the spring joint units of the other embodiments.
  • a spring 36 can also be seen from FIG. 5, which has a winding direction opposite the winding direction of the helical spring 19.
  • This spring 36 the stabilization spring can be referred to, extends over the area of the spring joint 13.
  • the outer diameter of the spring 36 corresponds to the inner diameter of the spring 19, so that the turns of the spring 36 bear against the turns of the coil spring 19. In this way, it is brought about that, after the spring joint 13 has deflected, the individual turns of the spring 19 always come to lie practically exactly on one another, so that the tilting rod practically always returns to the original position after being pivoted out. It is clear to the person skilled in the art that such a stabilizing spring 36 could also be used in the embodiment in FIG. 3.
EP83107254A 1982-07-28 1983-07-23 Piquet basculant Expired EP0100951B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT83107254T ATE30121T1 (de) 1982-07-28 1983-07-23 Kippstange.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH457682 1982-07-28
CH4576/82 1982-07-28

Publications (2)

Publication Number Publication Date
EP0100951A1 true EP0100951A1 (fr) 1984-02-22
EP0100951B1 EP0100951B1 (fr) 1987-10-07

Family

ID=4278671

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83107254A Expired EP0100951B1 (fr) 1982-07-28 1983-07-23 Piquet basculant

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EP (1) EP0100951B1 (fr)
AT (1) ATE30121T1 (fr)
DE (1) DE3373981D1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2628332A2 (fr) * 1987-08-03 1989-09-15 Charbonnier Jacques Axes a ressort pour ski a elements paralleles

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE124746C (fr) *
CH142477A (de) * 1929-12-21 1930-09-30 Amstutz Max Absteck-Feldzeichen.
US1890696A (en) * 1932-06-30 1932-12-13 Rosenhahn Carl Punching bag apparatus
US3276761A (en) * 1963-05-20 1966-10-04 Goetzewerke Tensile spring ring for shaft packings
DE2306421A1 (de) * 1973-02-09 1974-08-22 Tschelisnik Slalom-sicherheitstorstange
DE2310717A1 (de) * 1973-03-03 1974-09-12 Fritz Schoeggl Slalom-torstange
DE2524592A1 (de) * 1975-06-03 1976-12-23 Wilhelm Gronbach Stossdaempfer
EP0077313A1 (fr) * 1981-10-13 1983-04-20 LINDSKOG, Kjell Jan-Erik Piquet de slalom flexible

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3115741A1 (de) * 1981-04-18 1982-11-04 Gerd Dieter 7326 Heiningen Maibach Sicherheitsslalomstab

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE124746C (fr) *
CH142477A (de) * 1929-12-21 1930-09-30 Amstutz Max Absteck-Feldzeichen.
US1890696A (en) * 1932-06-30 1932-12-13 Rosenhahn Carl Punching bag apparatus
US3276761A (en) * 1963-05-20 1966-10-04 Goetzewerke Tensile spring ring for shaft packings
DE2306421A1 (de) * 1973-02-09 1974-08-22 Tschelisnik Slalom-sicherheitstorstange
DE2310717A1 (de) * 1973-03-03 1974-09-12 Fritz Schoeggl Slalom-torstange
DE2524592A1 (de) * 1975-06-03 1976-12-23 Wilhelm Gronbach Stossdaempfer
EP0077313A1 (fr) * 1981-10-13 1983-04-20 LINDSKOG, Kjell Jan-Erik Piquet de slalom flexible

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2628332A2 (fr) * 1987-08-03 1989-09-15 Charbonnier Jacques Axes a ressort pour ski a elements paralleles

Also Published As

Publication number Publication date
EP0100951B1 (fr) 1987-10-07
DE3373981D1 (en) 1987-11-12
ATE30121T1 (de) 1987-10-15

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